US12092403B2 - Heat exchanger - Google Patents

Heat exchanger Download PDF

Info

Publication number
US12092403B2
US12092403B2 US17/592,680 US202217592680A US12092403B2 US 12092403 B2 US12092403 B2 US 12092403B2 US 202217592680 A US202217592680 A US 202217592680A US 12092403 B2 US12092403 B2 US 12092403B2
Authority
US
United States
Prior art keywords
tubes
grooves
adjacent
portions
extending direction
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active, expires
Application number
US17/592,680
Other languages
English (en)
Other versions
US20220155028A1 (en
Inventor
Keita Morimoto
Eiichi Torigoe
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Denso Corp
Original Assignee
Denso Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Denso Corp filed Critical Denso Corp
Assigned to DENSO CORPORATION reassignment DENSO CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TORIGOE, EIICHI, MR., MORIMOTO, Keita
Publication of US20220155028A1 publication Critical patent/US20220155028A1/en
Application granted granted Critical
Publication of US12092403B2 publication Critical patent/US12092403B2/en
Active legal-status Critical Current
Adjusted expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1615—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits being inside a casing and extending at an angle to the longitudinal axis of the casing; the conduits crossing the conduit for the other heat exchange medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/30—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being attachable to the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0085—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2245/00—Coatings; Surface treatments
    • F28F2245/02—Coatings; Surface treatments hydrophilic

Definitions

  • the present disclosure relates to a heat exchanger.
  • a heat exchanger includes flat tubes and corrugated fins each of which is arranged between adjacent ones of the flat tubes.
  • the corrugated fins are joined to the flat tubes and an air flows through gaps of the corrugated fins.
  • Each of the corrugated fins defines multiple louvers as a heat transfer promoter.
  • Each of the corrugated fins further defines fluid passages on a surface of the corrugated fin between the louvers and a joint between the tube and the corrugated fin.
  • a heat exchanger includes a plurality of tubes through which a first fluid flows and a corrugated fin configured to improve heat exchange efficiency between the first fluid flowing through the plurality of tubes and a second fluid flowing outside of the plurality of tubes.
  • the corrugated fin includes a plurality of bending portions connected to adjacent two tubes of the plurality of tubes and a plurality of fin body portions each extending between the adjacent two tubes.
  • Each of the plurality of fin body portions defines a plurality of grooves on a surface thereof. Each of the plurality of grooves extends in an extending direction from one of the adjacent two tubes toward the other of the adjacent two tubes.
  • Each of the plurality of fin body portions includes a protrusion disposed at an intermediate position of at least one of the plurality of grooves between the adjacent two tubes in the extending direction.
  • the protrusion protrudes from a bottom of the at least one of the plurality of grooves toward the surface.
  • a heat exchanger includes a plurality of tubes through which a first fluid flows and a corrugated fin configured to improve heat exchange efficiency between the first fluid flowing through the plurality of tubes and a second fluid flowing outside of the plurality of tubes.
  • the corrugated fin includes a plurality of bending portions connected to adjacent two tubes of the plurality of tubes and a plurality of fin body portions each extending between the adjacent two tubes.
  • Each of the plurality of fin body portions defines a plurality of grooves each extending in an extending direction from one of the adjacent two tubes toward the other of the adjacent two tubes.
  • Each of the plurality of grooves between the adjacent two tubes has a predetermined width.
  • At least one of the plurality of grooves has a narrow portion at an intermediate position of the at least one of the plurality of grooves between the adjacent two tubes in the extending direction. The narrow portion has a width narrower than the predetermined width.
  • a heat exchanger includes a plurality of tubes through which a first fluid flows and a corrugated fin configured to improve heat exchange efficiency between the first fluid flowing through the plurality of tubes and a second fluid flowing outside of the plurality of tubes.
  • the corrugated fin includes a plurality of bending portions connected to adjacent two tubes of the plurality of tubes and a plurality of fin body portions each extending between the adjacent two tubes.
  • Each of the fin body portions defines a plurality of grooves on a surface thereof.
  • Each of the plurality of grooves extends in an extending direction from one of the adjacent two tubes toward the other of the adjacent two tubes. At least two of the plurality of grooves in parallel with each other are merged at a merging portion.
  • the merging portion is fluidly connected to one end of a hydrophilicity reducing portion in the extending direction.
  • An other end of the hydrophilicity reducing portion in the extending direction is fluidly connected to a branching portion from which at least two of the plurality of grooves in parallel with each other branch off.
  • the hydrophilicity reducing portion is configured to reduce a hydrophilicity of a portion of the surface between the merging portion and the branching portion to less than that of a portion of the surface where the at least two of the plurality of grooves merged at the merging portion and the at least two of the plurality of grooves branching from the branching portion are formed.
  • FIG. 1 is a perspective view of a heat exchanger according to a first embodiment.
  • FIG. 2 is a partially enlarged view of the heat exchanger.
  • FIG. 3 is a partially enlarged view of the heat exchanger.
  • FIG. 4 is a partially enlarged view of a corrugated fin.
  • FIG. 5 is a cross-sectional view taken along a line V-V in FIG. 4 .
  • FIG. 6 is a diagram illustrating a flow of condensed water in a comparative example that does not include a protrusion in an intermediate position of grooves.
  • FIG. 7 is a diagram illustrating a flow of condensed water in the comparative example that does not include the protrusion in the intermediate position of grooves.
  • FIG. 8 is a diagram illustrating a flow of condensed water in the heat exchanger according to the first embodiment.
  • FIG. 9 is a diagram illustrating a state of condensed water in the heat exchanger of the first embodiment.
  • FIG. 10 is a diagram illustrating a flow of condensed water in a configuration in which the protrusions are formed in intermediate positions of the grooves.
  • FIG. 11 is a diagram illustrating a state of condensed water in the configuration in which the protrusions are formed in the intermediate positions of the grooves.
  • FIG. 12 is a cross-sectional view of a corrugated fin of a heat exchanger of a second embodiment, which corresponds to FIG. 5 .
  • FIG. 13 is an external view of a fin body portion of a corrugated fin of a heat exchanger of a third embodiment that is viewed in a direction of an arrow XIII in FIG. 4 .
  • FIG. 14 is an external view of a fin body portion of a corrugated fin of a heat exchanger of a fourth embodiment, which corresponds to FIG. 13 .
  • FIG. 15 is an external view of a fin body portion of a corrugated fin of a heat exchanger of a fifth embodiment, which corresponds to FIG. 13 .
  • FIG. 16 is an external view of a corrugated fin of a heat exchanger according to a sixth embodiment.
  • FIG. 17 is a diagram schematically illustrating the corrugated fin of the heat exchanger according to the sixth embodiment.
  • FIG. 18 is a diagram illustrating an area where condensed water stays in the heat exchanger of the sixth embodiment.
  • FIG. 19 is a diagram of a corrugated fin of a heat exchanger of a comparative example relative to the sixth embodiment.
  • FIG. 20 is a diagram illustrating an area where condensed water stays in the corrugated fin of the comparative example.
  • FIG. 21 is a diagram for explaining a problem.
  • a heat exchanger includes flat tubes and corrugated fins each of which is arranged between adjacent ones of the flat tubes.
  • the corrugated fins are joined to the flat tubes and an air flows through gaps of the corrugated fins.
  • Each of the corrugated fins defines multiple louvers as a heat transfer promoter.
  • Each of the corrugated fins further defines fluid passages on a surface of the corrugated fin between the louvers and a joint between the tube and the corrugated fin. In this heat exchanger, water staying on peaks of the corrugated fin flows vertically downward through the fluid passages.
  • the heat exchanger cannot effectively drain the condensed water staying in a central portion of the corrugated fin between two adjacent flat tubes.
  • the corrugated fin 10 disposed between the adjacent two tubes 20 defines multiple grooves 900 on a surface of the corrugated fin 10 to improve hydrophilicity of the surface.
  • the grooves 900 can improve the surface of the hydrophilicity of the corrugated fin 10 , so that condensed water staying in the center portion C of the corrugated fin 10 between the adjacent two tubes 20 can be effectively drained.
  • the grooves may assist the condensed water in flowing to the center portion C of the corrugated fin 10 between the adjacent two tubes 20 . Actually, drainability is lowered.
  • a heat exchanger includes a plurality of tubes through which a first fluid flows and a corrugated fin configured to improve heat exchange efficiency between the first fluid flowing through the plurality of tubes and a second fluid flowing outside of the plurality of tubes.
  • the corrugated fin includes a plurality of bending portions connected to adjacent two tubes of the plurality of tubes and a plurality of fin body portions each extending between the adjacent two tubes.
  • Each of the plurality of fin body portions defines a plurality of grooves on a surface thereof. Each of the plurality of grooves extends in an extending direction from one of the adjacent two tubes toward the other of the adjacent two tubes.
  • Each of the plurality of fin body portions includes a protrusion disposed at an intermediate position of at least one of the plurality of grooves between the adjacent two tubes in the extending direction.
  • the protrusion protrudes from a bottom of the at least one of the plurality of grooves toward the surface.
  • the protrusion protruding from the bottom of the at least one of the plurality of grooves toward the surface is disposed at the intermediate position of the at least one of the grooves between the adjacent two tubes in the extending direction. Therefore, when the amount of the condensed water generated on the tubes is small, the condensed water from the tubes 20 can be inhibited from flowing to the center portion of the corrugated fin between the adjacent tubes.
  • a heat exchanger includes a plurality of tubes through which a first fluid flows and a corrugated fin configured to improve heat exchange efficiency between the first fluid flowing through the plurality of tubes and a second fluid flowing outside of the plurality of tubes.
  • the corrugated fin includes a plurality of bending portions connected to adjacent two tubes of the plurality of tubes and a plurality of fin body portions each extending between the adjacent two tubes.
  • Each of the plurality of fin body portions defines a plurality of grooves each extending in an extending direction from one of the adjacent two tubes toward the other of the adjacent two tubes.
  • Each of the plurality of grooves between the adjacent two tubes has a predetermined width.
  • At least one of the plurality of grooves has a narrow portion at an intermediate position of the at least one of the plurality of grooves between the adjacent two tubes in the extending direction. The narrow portion has a width narrower than the predetermined width.
  • At least one of the plurality of grooves has the narrow portion at the intermediate position thereof in the extending direction.
  • the narrow portion has a width narrower than the predetermined width. Therefore, when the amount of the condensed water generated on the tubes is small, the condensed water from the tubes can be inhibited from flowing to the center portion of the corrugated fin between the adjacent tubes.
  • a heat exchanger includes a plurality of tubes through which a first fluid flows and a corrugated fin configured to improve heat exchange efficiency between the first fluid flowing through the plurality of tubes and a second fluid flowing outside of the plurality of tubes.
  • the corrugated fin includes a plurality of bending portions connected to adjacent two tubes of the plurality of tubes and a plurality of fin body portions each extending between the adjacent two tubes.
  • Each of the fin body portions defines a plurality of grooves on a surface thereof.
  • Each of the plurality of grooves extends in an extending direction from one of the adjacent two tubes toward the other of the adjacent two tubes. At least two of the plurality of grooves in parallel with each other are merged at a merging portion.
  • the merging portion is fluidly connected to one end of a hydrophilicity reducing portion in the extending direction.
  • An other end of the hydrophilicity reducing portion in the extending direction is fluidly connected to a branching portion from which at least two of the plurality of grooves in parallel with each other branch off.
  • the hydrophilicity reducing portion is configured to reduce a hydrophilicity of a portion of the surface between the merging portion and the branching portion to less than that of a portion of the surface where the at least two of the plurality of grooves merged at the merging portion and the at least two of the plurality of grooves branching from the branching portion are formed.
  • the merging portion is fluidly connected to one end of the hydrophilicity reducing portion in the extending direction.
  • the other end of the hydrophilicity reducing portion in the extending direction is fluidly connected to the branching portion from which at least two of the plurality of grooves in parallel with each other branch off.
  • the hydrophilicity reducing portion is configured to reduce a hydrophilicity of a portion of the surface between the merging portion and the branching portion to less than that of a portion of the surface where the at least two of the plurality of grooves merged at the merging portion and the at least two of the plurality of grooves branching from the branching portion are formed. Therefore, when the amount of the condensed water generated on the tubes is small, the condensed water from the tubes can be inhibited from flowing to the center portion of the corrugated fin between the adjacent tubes.
  • a heat exchanger 1 is used, for example, as an evaporator configuring a part of a refrigeration cycle for performing air-conditioning in a vehicle compartment.
  • the evaporator performs a heat exchange between a refrigerant as a first fluid circulating in the refrigeration cycle and an air as a second fluid passing through the heat exchanger 1 , and cools the air by a latent heat of evaporation of the refrigerant.
  • a flow direction of the air passing through the heat exchanger 1 is indicated by an arrow AF.
  • the heat exchanger 1 includes corrugated fins 10 , tubes 20 , a first header tank 21 , a second header tank 22 , a third header tank 23 , a fourth header tank 24 , outer frame members 25 , a pipe connection member 26 , and the like.
  • Those members are made of aluminum, for example, and the members are joined to each other by brazing.
  • the multiple tubes 20 are arranged at predetermined intervals in a direction intersecting with an airflow direction.
  • the multiple tubes 20 are arranged in two rows on an upstream side and a downstream side in the airflow direction.
  • Each of the multiple tubes 20 extends linearly from one end to the other end.
  • One end of the multiple tubes 20 is inserted into the first header tank 21 or the second header tank 22 , and the other end is inserted into the third header tank 23 or the fourth header tank 24 .
  • the first header tank 21 , the second header tank 22 , the third header tank 23 , and the fourth header tank 24 distribute the refrigerant to the multiple tubes 20 and collect the refrigerant flowing in from the multiple tubes 20 .
  • the multiple tubes 20 define air passages through which an air flows therebetween.
  • the corrugated fins 10 are provided respectively in the air passages.
  • the corrugated fins 10 according to the present embodiment are outer fins provided on the outside of the tubes 20 .
  • the corrugated fins 10 increase a heat transfer area between the refrigerant flowing inside the tubes 20 and the air flowing outside the tubes 20 , to thereby enhance a heat exchange efficiency between the refrigerant and the air.
  • the outer frame members 25 are provided outside of the multiple tubes 20 and the multiple corrugated fins 10 in a direction in which the multiple tubes 20 and the multiple corrugated fins 10 are alternately arranged.
  • the pipe connection member 26 is fixed to the outer frame member 25 .
  • the pipe connection member 26 defines a refrigerant inlet 27 into which the refrigerant is supplied and a refrigerant outlet 28 for discharging the refrigerant.
  • the refrigerant flows into the first header tank 21 through the refrigerant inlet 27 , flows through the first header tank 21 , the second header tank 22 , the third header tank 23 , the fourth header tank 24 , and the multiple tubes 20 in a predetermined path, and flows out through the refrigerant outlet 28 .
  • a latent heat of evaporation of the refrigerant flowing through the first to fourth header tanks 21 to 24 and the multiple tubes 20 cools the air flowing through the air passages in which the corrugated fins 10 are arranged.
  • FIGS. 2 and 3 are enlarged views of the corrugated fin 10 .
  • the corrugated fin 10 has a configuration in which a plate-shaped member 100 is bent at predetermined intervals.
  • the corrugated fin 10 has multiple bending portions 12 and fin body portions 13 .
  • the multiple bending portions 12 are portions in which the plate-shaped member 100 configuring the corrugated fin 10 is bent at predetermined intervals.
  • the fin body portions 13 are portions disposed between the bending portion 12 and the bending portion 12 .
  • Each of the fin body portions 13 defines multiple louvers 14 each formed by cutting and bending a part of the plate-shaped member 100 .
  • An outer wall of the corrugated fin 10 facing the tube 20 is joined to an outer wall of the tube 20 by brazing.
  • the surface of the corrugated fin 10 defines fine grooves 11 for increasing hydrophilicity. Specifically, the fine grooves 11 are defined on both surfaces of the plate-shaped member 100 .
  • the multiple grooves 11 are arranged at predetermined intervals to be separated away from each other.
  • the multiple grooves 11 defined on the surfaces of the corrugated fin 10 are schematically largely illustrated for the sake of description. This also applies to the drawings referred to in second to sixth embodiments which will be described later.
  • the multiple grooves 11 are defined in the bending portions 12 and the fin body portions 13 of the corrugated fin 10 .
  • the multiple grooves 11 are also defined in the louvers 14 .
  • the multiple grooves 11 extend from the bent portion 12 joined to one tube 20 toward the bent portion 12 joined to another tube 20 .
  • a width of each of the grooves 11 is preferably within a range of 10 to 50 ⁇ m.
  • a depth of each of the grooves 11 is preferably 10 ⁇ m or more.
  • a pitch of the grooves 11 is preferably within a range of 50 to 200 ⁇ m.
  • the hydrophilicity of the surface of the corrugated fin 10 can be improved.
  • the ventilation resistance of the air passages can avoid increasing due to the condensed water staying in the air passages, so that the heat exchanger 1 can improve the heat exchanging performance.
  • the corrugated fin 10 of the present embodiment includes two protrusions 111 arranged in an intermediate position of each of the multiple grooves 11 between the two bending portions 12 joined to the two tubes 20 .
  • the two protrusions 111 protrude to reach the surface 10 a of the corrugated fin 10 .
  • the protrusions 111 divide each of the grooves 11 at two points between the two bending portions 12 joined to the two tubes 20 .
  • FIG. 21 illustrates the configuration in which the protrusion 111 like the present embodiment is not formed in the intermediate position of the grooves 11 .
  • the condensed water Wc generated on the tube 20 flows downward as shown in an arrow FL 1 in FIG. 6 .
  • the condensed water staying on the center portion of the corrugated fin 10 between the two tubes 20 flows toward the tube 20 through the grooves 11 as shown in an arrow FL 3 in FIG. 6 .
  • the protrusions 111 are formed at an intermediate position of each of the grooves 11 between the bending portions 12 joined to the two tubes 20 .
  • the condensed water Wc generated on the tube 20 can be inhibited from flowing to the central portion of the corrugated fin 10 between the two tubes 20 . That is, the protrusions 111 formed at the intermediate positions of the grooves 11 can inhibit the condensed water generated on the tube 20 from flowing to the center portion of the corrugated fin 10 between the two tubes 20 .
  • the heat exchanger 1 of the present embodiment includes a plurality of tubes 20 through which a first fluid flows. Further, the heat exchanger 1 includes a corrugated fin 10 configured to improve heat change efficiency between the first fluid flowing through the tubes 20 and a second fluid flowing outside of the tubes 20 . Further, the corrugated fin 10 includes a plurality of bending portions 12 connected adjacent two tubes 20 of the plurality of tubes 20 . Further, the corrugated fin 10 includes a plurality of fin body portions 13 each extending between the adjacent two tubes 20 . Further, each of the plurality of fin body portions 13 defines a plurality of grooves 11 on a surface thereof.
  • Each of the plurality of fin body portions 13 extends in an extending direction from one of the adjacent two tubes 20 toward the other of the adjacent two tubes 20 .
  • Each of the plurality of fin body portions 13 further includes the plurality of protrusions 111 disposed at intermediate positions of the plurality of grooves 11 in the extending direction.
  • Each of the plurality of protrusions 111 protrudes from a bottom 110 of the groove 11 toward the surface 10 a of each of the plurality of fin body portions 13 .
  • the corrugated fin 10 includes the protrusions 111 at intermediate positions of the grooves 11 in the extending direction.
  • Each of the protrusions 111 protrude from the bottom 110 of the groove 11 toward the surface 10 a of the fin body portion 13 . Therefore, when the amount of the condensed water on the tube 20 is small, the condensed water from the tubes 20 can be inhibited from flowing to reach the center portion of the corrugated fin 10 between the adjacent two tubes 20 .
  • each of the protrusions 111 protrudes from the bottom 110 of the groove 11 to reach the surface 10 a of the corrugated fin 10 .
  • a hydrophilicity of an area where the protrusion 111 is formed is greatly decreased, so that the condensed water from the tubes 20 is more effectively inhibited from flowing to the center portion of the corrugated fin 10 between the adjacent tubes 20 .
  • each of the plurality of grooves 11 has at least two protrusions 111 at intermediate positions in the extending direction.
  • a heat exchanger 1 of a second embodiment will be described with reference to FIG. 12 .
  • the protrusion 111 of the first embodiment protrudes from the bottom 110 of the groove 11 to reach the surface 10 a of the corrugated fin 10 .
  • the protrusion 111 protrudes from the bottom 110 of the groove 11 to a position lower than the surface 10 a of the corrugated fin 10 .
  • the condensed water Wc generated on the tube 20 can be inhibited from flowing to the center portion of the corrugated fin 10 between the two tubes 20 .
  • the present embodiment can achieve the effects and advantages which are obtained from the structure common to the first embodiment.
  • a heat exchanger 1 of a third embodiment will be described with reference to FIG. 13 .
  • narrow portions 112 each having a width narrower than that of each of the grooves 11 are provided.
  • Each of the grooves 11 extending between the adjacent two tubes 20 has a predetermined width.
  • each of the grooves 11 has narrow portions 112 at an intermediate position of each of the grooves 11 in the extending direction.
  • Each of the narrow portions 112 has a width narrower than the predetermined width.
  • the narrow portions 112 inhibit the condensed water generated on the tubes 20 from flowing to the center portion of the corrugated fin 10 between the two tubes 20 . That is, the narrow portions 112 formed at the intermediate position of each of the grooves 11 inhibit the condensed water generated on the tubes 20 from flowing to reach the center portion of the corrugated fin 10 between the tubes 20 .
  • the heat exchanger 1 of the present embodiment includes a plurality of tubes 20 through which a first fluid flows. Further, the heat exchanger 1 includes a corrugated fin 10 configured to improve heat change efficiency between the first fluid flowing through the tubes 20 and a second fluid flowing outside of the tubes 20 . Further, the corrugated fin 10 includes a plurality of bending portions 12 connected adjacent two tubes 20 of the plurality of tubes 20 . Further, the corrugated fin 10 includes a plurality of fin body portions 13 each extending between the adjacent two tubes 20 . Further, each of the fin body portions 13 defines multiple grooves 11 each extending in an extending direction from one of the adjacent two tubes 20 toward the other of the adjacent two tubes 20 .
  • each of the grooves 11 between the adjacent two tubes 20 has a predetermined width. Then, each of the grooves 11 has the narrow portions 112 disposed at an intermediate position of each of the grooves 11 in the extending direction. Each of the narrow portions 112 has a width narrower than the predetermined width.
  • each of the grooves 11 has the narrow portions 112 at an intermediate position of each of the grooves 11 in the extending direction.
  • Each of the narrow portions 112 has a width narrower than the predetermined width. Therefore, when the amount of the condensed water on the tubes 20 is small, the condensed water from the tubes 20 can be inhibited from flowing to reach the center portion of the corrugated fin 10 between the adjacent two tubes 20 .
  • the condensed waters on both sides of the narrow portion 112 are connected through the condensed water on the narrow portion 112 .
  • the condensed water staying on the center portion of the corrugated fin 10 between the two tubes 20 flows over the narrow portion 112 and further flows downward. Therefore, drainability can be ensured.
  • each of the grooves 11 has two narrow portions 112 at intermediate positions of each of the grooves 11 in the extending direction.
  • a heat exchanger 1 of a fourth embodiment will be described with reference to FIG. 14 .
  • the heat exchanger 1 of the present embodiment is different from the heat exchanger 1 of the first embodiment in that at least one of the grooves 11 does not include the protrusion 111 .
  • At least one of the grooves 11 does not have to include the protrusion 111 .
  • the present embodiment can achieve the effects and advantages which are obtained from the structure common to the first embodiment.
  • a heat exchanger 1 of a fifth embodiment will be described with reference to FIG. 15 .
  • the heat exchanger 1 of the present embodiment includes a merging portion 113 a and a branching portion 113 b that are arranged at an intermediate position of each of the fin body portions 13 between the adjacent two tubes 20 .
  • At least two grooves 11 in parallel with each other of the grooves 11 are merged at the merging portion 113 a .
  • At least two grooves 11 in parallel with each other of the grooves 11 branch off from the branching portion 113 b .
  • the merging portion 113 a and the branching portion 113 b are fluidly connected to each other.
  • the merging portion 113 a and the branching portion 113 b are fluidly connected through a hydrophilicity reducing portion 113 .
  • the hydrophilicity reducing portion 113 is configured to reduce a hydrophilicity of a portion of the surface of the corrugated fin 10 between the merging portion 113 a and the branching portion 113 b to less than that of a portion of the surface where the grooves 11 are formed.
  • the hydrophilicity reducing portion 113 can inhibit the condensed water generated on the tubes 20 from flowing to reach the center portion of the corrugated fin 10 between the adjacent tubes 20 .
  • hydrophilicity reducing portions 113 arranged in the extending direction between the two tubes 20 .
  • the heat exchanger 1 of the present embodiment includes a plurality of tubes 20 through which a first fluid flows. Further, the heat exchanger 1 includes the corrugated fin 10 configured to improve heat change efficiency between the first fluid flowing through the tubes 20 and the second fluid flowing outside of the tubes 20 . Further, the corrugated fin 10 includes a plurality of bending portions 12 connected to adjacent two tubes of the plurality of tubes 20 and a plurality of fin body portions 13 each extending between the adjacent two tubes 20 . Further, each of the plurality of fin body portions 13 defines a plurality of grooves 11 on a surface thereof. Each of the plurality of fin body portions 13 extends in an extending direction from one of the adjacent two tubes 20 toward the other of the adjacent two tubes 20 .
  • the merging portion 113 a is fluidly connected to one end of a hydrophilicity reducing portion in the extending direction.
  • An other end of the hydrophilicity reducing portion 113 in the extending direction is fluidly connected to a branching portion from which at least two of the plurality of grooves 11 in parallel with each other branch off.
  • the hydrophilicity reducing portion 113 is configured to reduce a hydrophilicity of a portion of the surface between the merging portion 113 a and the branching portion to less than that of a portion of the surface where the at least two of the plurality of grooves merged at the merging portion 113 a and the at least two of the plurality of grooves branching from the branching portion 113 b are formed.
  • the merging portion 113 a and the branching portion 113 b are formed at an intermediate portion of each of the plurality of fin body portions in the extending direction.
  • the hydrophilicity reducing portion 113 is configured to reduce a hydrophilicity of a portion of the surface between the merging portion 113 a and the branching portion 113 b to less than that of a portion of the surface where the at least two of the plurality of grooves merged at the merging portion 113 a and the at least two of the plurality of grooves branching from the branching portion 113 b are formed. Therefore, when the amount of the condensed water on the tube 20 is small, the condensed water from the tubes 20 can be inhibited from flowing to reach the center portion of the corrugated fin 10 between the adjacent two tubes 20 .
  • hydrophilicity reducing portions 113 arranged at the intermediate portion in the extending direction between the adjacent two tubes 20 .
  • FIGS. 17 to 20 are diagrams of each of the fin body portions 13 and the adjacent two tubes 20 viewed in an XVII direction in FIG. 2 . Further, each of FIGS. 17 to 20 illustrates a state in which the plate-shaped member 100 before the louvers 14 are formed is arranged between the adjacent two tubes 20 . It should be noted that FIGS. 17 to 20 illustrate grooves 140 for forming the louvers 14 .
  • the protrusions 111 are diagonally arranged from one of the adjacent two tubes 20 toward the other of the adjacent two tubes 20 relative to a direction perpendicular to the extending direction of the grooves 11 along the surface of each of the fin body portions 13 . That is, in the heat exchanger 1 , as shown in FIG. 17 , the areas where the protrusions 111 are formed are diagonally arranged between the adjacent two tubes 20 .
  • the condensed water generated on the tube 20 is blocked in the area where the protrusions 111 are formed, retained in an area Ar, and flows downward through a gap of the louver 14 .
  • the area Ar where the condensed water is retained is relatively small. Thus, better drainability can be obtained.
  • FIG. 19 illustrates a comparative example in which the areas where the protrusions 111 are arranged in a direction perpendicular to the extending direction of the grooves 11 along the surface of each of the fin body portions 13 .
  • the protrusions 111 are diagonally arranged from one of the adjacent two tubes 20 toward the other of the adjacent two tubes 20 relative to a direction perpendicular to the extending direction of the grooves 11 along the surface of each of the fin body portions 13 .
  • areas where the narrow portions 112 or the hydrophilicity reducing portions 113 are formed may be diagonally arranged from one of the adjacent two tubes 20 to the other of the adjacent two tubes 20 relative to the direction perpendicular to the extending direction of the grooves 11 along the surface of the each of the fin body portions 13 .
  • each of the grooves 11 has two protrusions 111 or two narrow portions 112 .
  • two hydrophilicity reducing portions 113 are arranged in the extending direction.
  • the number of the protrusions 111 , the narrow portions 112 , and the hydrophilicity reducing portions 113 is not limited to two.
  • the narrow portion 112 having a width narrower than that of the groove 11 is arranged in an intermediate position of each of the grooves 11 .
  • the width of the narrow portion 112 may be zero. That is, each of the grooves 11 may be divided into three grooves by the narrow portions 112 .
  • a quantity, a value, an amount, a range, or the like, if specified in the above-described example embodiments, is not necessarily limited to the specific value, amount, range, or the like unless it is specifically stated that the value, amount, range, or the like is necessarily the specific value, amount, range, or the like, or unless the value, amount, range, or the like is obviously necessary to be the specific value, amount, range, or the like in principle.
  • the heat exchanger includes a plurality of tubes through which a first fluid flows.
  • the heat exchanger further includes a corrugated fin that is configured to improve heat exchange efficiency between the first fluid flowing through the plurality of tubes and a second fluid flowing outside of the plurality of tubes.
  • the corrugated fin has a plurality of bending portions connected adjacent two tubes of the plurality of tubes.
  • the corrugated fin has a plurality of fin body portions each arranged between the adjacent two tubes.
  • each of the plurality of fin body portions defines a plurality of grooves on a surface thereof. Each of the plurality of grooves extends in an extending direction from one of the adjacent two tubes toward the other of the adjacent two tubes.
  • each of the plurality of fin plurality of fin body portions includes a protrusion disposed at an intermediate position of at least one of the plurality of grooves in the extending direction.
  • the protrusion protrudes from a bottom of the at least one of the plurality of grooves toward the surface of each of the plurality of fin body portions.
  • the protrusion protrudes from the bottom of the at least one of the grooves to reach the surface of the corrugated fin.
  • the protrusion includes at least two protrusions arranged at intermediate positions of one of the multiple grooves between the adjacent two tubes in the extending direction.
  • each of the fin body portions includes multiple louvers each formed by cutting and bending a part of each of the fin body portions.
  • the protrusions of each of the fin body portions are diagonally arranged from one of the adjacent two tubes toward the other of the adjacent two tubes relative to a direction perpendicular to the extending direction of the grooves along the surface of each of the fin body portions.
  • the heat exchanger includes multiple tubes through which a first fluid flows.
  • the heat exchanger further includes a corrugated fin that is configured to improve heat exchange efficiency between the first fluid flowing through the tubes and a second fluid flowing outside of the tubes.
  • the corrugated fin has multiple bending portions connected adjacent two tubes of the multiple tubes.
  • the corrugated fin has multiple fin body portions each arranged between the adjacent two tubes.
  • each of the fin body portions defines multiple grooves each extending in an extending direction from one of the adjacent two tubes toward the other of the adjacent two tubes.
  • each of the grooves between the adjacent two tubes has a predetermined width.
  • at least one of the grooves has a narrow portion at an intermediate position thereof in the extending direction. The narrow portion has a width narrower than the predetermined width.
  • the narrow portions includes at least two narrow portions arranged at intermediate positions of one of the grooves between the adjacent two tubes in the extending direction.
  • each of the fin body portions includes multiple louvers each formed by cutting and bending a part of each of the fin body portions.
  • the narrow portion is multiple narrow portions formed in the grooves. The narrow portions are diagonally arranged from one of the adjacent two tubes toward the other of the adjacent two tubes relative to a direction perpendicular to the extending direction of the grooves along the surface of each of the fin body portions.
  • the heat exchanger includes multiple tubes through which a first fluid flows.
  • the heat exchanger further includes a corrugated fin that is configured to improve heat exchange efficiency between the first fluid flowing through the tubes and a second fluid flowing outside of the tubes.
  • the corrugated fin has multiple bending portions connected adjacent two tubes of the multiple tubes.
  • the corrugated fin has multiple fin body portions each arranged between the adjacent two tubes.
  • each of the fin body portions defines multiple grooves on a surface thereof. Each of the multiple grooves extends in an extending direction from one of the adjacent two tubes toward the other of the adjacent two tubes.
  • each of the fin body portions includes a merging portion at which at least two of the grooves in parallel with each other are merged.
  • the merging portion is fluidly connected to one end of a hydrophilicity reducing portion in the extending direction.
  • An other end of the hydrophilicity reducing portion is fluidly connected to a branching portion from which at least two of the plurality of grooves in parallel with each other branch off.
  • the hydrophilicity reducing portion is configured to reduce a hydrophilicity of a portion of the surface between the merging portion and the branching portion 113 b to less than that of a portion of the surface where the at least two of the grooves merging at the merging portion and the at least two of the grooves branching off from the branching portion are formed.
  • the hydrophilicity reducing portion is a plurality of hydrophilicity reducing portions.
  • each of the fin body portions includes multiple louvers each formed by cutting and bending a part of each of the fin body portions.
  • the hydrophilicity reducing portions are diagonally arranged from one of the adjacent two tubes toward the other of the adjacent two tubes relative to a direction perpendicular to the extending direction of the grooves along the surface of each of the fin body portions.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US17/592,680 2019-08-06 2022-02-04 Heat exchanger Active 2041-05-23 US12092403B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2019144656A JP7263970B2 (ja) 2019-08-06 2019-08-06 熱交換器
JP2019-144656 2019-08-06
PCT/JP2020/029541 WO2021024958A1 (ja) 2019-08-06 2020-07-31 熱交換器

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2020/029541 Continuation WO2021024958A1 (ja) 2019-08-06 2020-07-31 熱交換器

Publications (2)

Publication Number Publication Date
US20220155028A1 US20220155028A1 (en) 2022-05-19
US12092403B2 true US12092403B2 (en) 2024-09-17

Family

ID=74503822

Family Applications (1)

Application Number Title Priority Date Filing Date
US17/592,680 Active 2041-05-23 US12092403B2 (en) 2019-08-06 2022-02-04 Heat exchanger

Country Status (5)

Country Link
US (1) US12092403B2 (enrdf_load_stackoverflow)
JP (1) JP7263970B2 (enrdf_load_stackoverflow)
CN (1) CN114207374B (enrdf_load_stackoverflow)
DE (1) DE112020003723T5 (enrdf_load_stackoverflow)
WO (1) WO2021024958A1 (enrdf_load_stackoverflow)

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59109418A (ja) 1982-12-15 1984-06-25 Nippon Denso Co Ltd 自動車用空調装置の内外気切換装置
US5201367A (en) * 1990-02-20 1993-04-13 Dubrovsky Evgeny V Stack of plates for a plate-and-tube heat exchanger with diverging-converging passages
US6889759B2 (en) * 2003-06-25 2005-05-10 Evapco, Inc. Fin for heat exchanger coil assembly
US20070251681A1 (en) * 2004-10-13 2007-11-01 Naohisa Higashiyama Evaporator
US7475719B2 (en) * 2006-12-14 2009-01-13 Evapco, Inc. High-frequency, low-amplitude corrugated fin for a heat exchanger coil assembly
JP2010025477A (ja) 2008-07-22 2010-02-04 Daikin Ind Ltd 熱交換器
US20120318485A1 (en) * 2010-02-25 2012-12-20 Mitsuo Yabe Corrugated fin and heat exchanger including the same
JP2013245883A (ja) 2012-05-28 2013-12-09 Panasonic Corp フィンチューブ熱交換器
US20160348987A1 (en) * 2014-02-14 2016-12-01 Sumitomo Precision Products Co., Ltd. Plate fin heat exchanger and manufacturing method for heat exchanger corrugated fins
WO2018230431A1 (ja) * 2017-06-12 2018-12-20 株式会社デンソー 熱交換器およびコルゲートフィン
JP2019002588A (ja) * 2017-06-12 2019-01-10 株式会社デンソー 熱交換器及びコルゲートフィン
JP2019002589A (ja) * 2017-06-12 2019-01-10 株式会社デンソー 熱交換器およびコルゲートフィン
JP2019163921A (ja) 2018-03-14 2019-09-26 株式会社デンソー 熱交換器
US20200096226A1 (en) 2017-06-12 2020-03-26 Denso Corporation Heat exchanger and corrugated fin

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000241093A (ja) * 1999-02-24 2000-09-08 Daikin Ind Ltd 空気熱交換器
JP2003336988A (ja) * 2002-05-20 2003-11-28 Japan Climate Systems Corp 熱交換器
JP2004060934A (ja) * 2002-07-25 2004-02-26 Toyo Radiator Co Ltd 蒸発器
CN1566889A (zh) * 2003-06-17 2005-01-19 乐金电子(天津)电器有限公司 热交换器的冷凝水排出装置
JP5417718B2 (ja) * 2007-03-07 2014-02-19 ダイキン工業株式会社 熱交換器
CN101598514A (zh) * 2008-06-06 2009-12-09 三花丹佛斯（杭州）微通道换热器有限公司 热交换器及其散热管
KR20100110036A (ko) * 2009-04-02 2010-10-12 엘지전자 주식회사 열교환기 및 그 제조방법
CN102235735B (zh) * 2010-05-05 2013-12-04 约克（无锡）空调冷冻设备有限公司 用于热泵系统的换热器
CN202057209U (zh) * 2011-04-15 2011-11-30 江苏宝得换热设备有限公司 一种换热器
JP2013190169A (ja) * 2012-03-14 2013-09-26 Sharp Corp 熱交換器
US10168102B2 (en) * 2012-10-16 2019-01-01 Mitsubishi Electric Corporation Plate type heat exchanger and refrigeration cycle apparatus having the same plate type heat exchanger
CN105987540A (zh) * 2015-02-10 2016-10-05 上海交通大学 管片式平行流换热器
CN104964487B (zh) * 2015-05-18 2017-12-19 广东美的制冷设备有限公司 热交换器、空调器及金属箔的加工方法
CN109539852A (zh) * 2017-09-22 2019-03-29 浙江盾安机械有限公司 一种微通道换热器的扁管以及微通道换热器
JP6839673B2 (ja) 2018-02-16 2021-03-10 日本電信電話株式会社 アプリケーション分割装置、方法およびプログラム

Patent Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59109418A (ja) 1982-12-15 1984-06-25 Nippon Denso Co Ltd 自動車用空調装置の内外気切換装置
US5201367A (en) * 1990-02-20 1993-04-13 Dubrovsky Evgeny V Stack of plates for a plate-and-tube heat exchanger with diverging-converging passages
US6889759B2 (en) * 2003-06-25 2005-05-10 Evapco, Inc. Fin for heat exchanger coil assembly
US20070251681A1 (en) * 2004-10-13 2007-11-01 Naohisa Higashiyama Evaporator
US7475719B2 (en) * 2006-12-14 2009-01-13 Evapco, Inc. High-frequency, low-amplitude corrugated fin for a heat exchanger coil assembly
JP2010025477A (ja) 2008-07-22 2010-02-04 Daikin Ind Ltd 熱交換器
US20120318485A1 (en) * 2010-02-25 2012-12-20 Mitsuo Yabe Corrugated fin and heat exchanger including the same
JP2013245883A (ja) 2012-05-28 2013-12-09 Panasonic Corp フィンチューブ熱交換器
US20160348987A1 (en) * 2014-02-14 2016-12-01 Sumitomo Precision Products Co., Ltd. Plate fin heat exchanger and manufacturing method for heat exchanger corrugated fins
JP6225042B2 (ja) 2014-02-14 2017-11-01 住友精密工業株式会社 プレートフィン熱交換器、及び、熱交換器用コルゲートフィンの製造方法
WO2018230431A1 (ja) * 2017-06-12 2018-12-20 株式会社デンソー 熱交換器およびコルゲートフィン
JP2019002588A (ja) * 2017-06-12 2019-01-10 株式会社デンソー 熱交換器及びコルゲートフィン
JP2019002589A (ja) * 2017-06-12 2019-01-10 株式会社デンソー 熱交換器およびコルゲートフィン
US20200096226A1 (en) 2017-06-12 2020-03-26 Denso Corporation Heat exchanger and corrugated fin
US20200096264A1 (en) 2017-06-12 2020-03-26 Denso Corporation Heat exchanger and corrugated fin
JP2019163921A (ja) 2018-03-14 2019-09-26 株式会社デンソー 熱交換器

Also Published As

Publication number Publication date
JP7263970B2 (ja) 2023-04-25
US20220155028A1 (en) 2022-05-19
DE112020003723T5 (de) 2022-06-09
JP2021025717A (ja) 2021-02-22
CN114207374B (zh) 2024-05-07
WO2021024958A1 (ja) 2021-02-11
CN114207374A (zh) 2022-03-18

Similar Documents

Publication Publication Date Title
US7726387B2 (en) Heat exchangers
US10352598B2 (en) Heat exchanger, in particular a condenser
US7886812B2 (en) Heat exchanger having a tank partition wall
US7635019B2 (en) Heat exchanger
US12228351B2 (en) Heat exchanger and corrugated fin
US6431264B2 (en) Heat exchanger with fluid-phase change
JP2007113802A (ja) 蒸発器
JP7188128B2 (ja) 熱交換器
WO2011049015A1 (ja) エバポレータ
JP6160385B2 (ja) 積層型熱交換器
JP6558268B2 (ja) 冷媒蒸発器
US12092403B2 (en) Heat exchanger
CN100432579C (zh) 蒸发器
US12007183B2 (en) Heat exchanger
JP6795012B2 (ja) 熱交換器およびコルゲートフィン
JP2006207994A (ja) エバポレータ
JP7006376B2 (ja) 熱交換器
JP3677898B2 (ja) 複式熱交換器
WO2019167839A1 (ja) 熱交換器
TWI809718B (zh) 熱交換器及冷凍循環裝置
WO2018008134A1 (ja) 熱交換器
WO2020184198A1 (ja) 熱交換器
JP2005083653A (ja) 冷媒蒸発器
JP2005069669A (ja) エバポレータ用コルゲートフィンおよびエバポレータ
JP2006084096A (ja) 細径多管式熱交換器の細径伝熱管ユニット

Legal Events

Date Code Title Description
AS Assignment

Owner name: DENSO CORPORATION, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:MORIMOTO, KEITA;TORIGOE, EIICHI, MR.;SIGNING DATES FROM 20211206 TO 20211228;REEL/FRAME:058887/0552

FEPP Fee payment procedure

Free format text: ENTITY STATUS SET TO UNDISCOUNTED (ORIGINAL EVENT CODE: BIG.); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

STPP Information on status: patent application and granting procedure in general

Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION

STPP Information on status: patent application and granting procedure in general

Free format text: NON FINAL ACTION MAILED

STPP Information on status: patent application and granting procedure in general

Free format text: RESPONSE TO NON-FINAL OFFICE ACTION ENTERED AND FORWARDED TO EXAMINER

STPP Information on status: patent application and granting procedure in general

Free format text: NOTICE OF ALLOWANCE MAILED -- APPLICATION RECEIVED IN OFFICE OF PUBLICATIONS

STPP Information on status: patent application and granting procedure in general

Free format text: PUBLICATIONS -- ISSUE FEE PAYMENT RECEIVED

STCF Information on status: patent grant

Free format text: PATENTED CASE